EP2636872B1 - Dispositif d'entraînement d'une turbomachine - Google Patents

Dispositif d'entraînement d'une turbomachine Download PDF

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Publication number
EP2636872B1
EP2636872B1 EP13157705.8A EP13157705A EP2636872B1 EP 2636872 B1 EP2636872 B1 EP 2636872B1 EP 13157705 A EP13157705 A EP 13157705A EP 2636872 B1 EP2636872 B1 EP 2636872B1
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EP
European Patent Office
Prior art keywords
hydraulic log
generator
motor
hydraulic
valve
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EP13157705.8A
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German (de)
English (en)
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EP2636872A3 (fr
EP2636872A2 (fr
Inventor
Eric A. Brust
Jr. Glenn C. Lemmers
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Hamilton Sundstrand Corp
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Hamilton Sundstrand Corp
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Priority claimed from US13/411,920 external-priority patent/US9394831B2/en
Application filed by Hamilton Sundstrand Corp filed Critical Hamilton Sundstrand Corp
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Publication of EP2636872A3 publication Critical patent/EP2636872A3/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/32—Arrangement, mounting, or driving, of auxiliaries
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/06—Purpose of the control system to match engine to driven device
    • F05D2270/061—Purpose of the control system to match engine to driven device in particular the electrical frequency of driven generator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • This disclosure relates generally to a drive arrangement for a turbomachine. More particularly, this disclosure relates to an arrangement that drives the turbomachine during a first mode of operation and generates electric power using the turbomachine in a second mode of operation.
  • Turbomachines such as gas turbine engines are known.
  • a typical turbomachine includes multiple sections, such as a fan section, a compression section, a combustor section, and a turbine section.
  • Many turbomachines, particularly gas turbine engines have large rotors in the compression section that must be accelerated to high rotational speeds until the rotor is rotating fast enough to sustain operation of the turbomachine.
  • a motor separate from the turbomachine drives an input shaft that is used to accelerate the rotors.
  • turbomachines use generators to produce electric power for various components, such as components on an aircraft.
  • Some turbomachines use generators separate from the motor that drives the rotors.
  • Integrated drive generators IDGs are an example of this type of generator, which can produce constant frequency electric power.
  • the generator separate from the motor undesirably adds weight and complexity to the turbomachine.
  • VFSG variable frequency starter generator
  • VFSGs generate electric output power with a frequency that is proportional to the turbomachine speed.
  • Electrical usage equipment must then be capable of operating under this variable frequency input, which generally increases their weight, envelope, power losses, and cost.
  • Some arrangements of this type include complicated shafting, gearing, clutching, or valving to enable both start and generate modes of operation.
  • US 4 315 442 discloses a hydraulic control system including a first and second hydraulic unit and a valve to control flow between the first and second units.
  • US 4 922 119 discloses a starting system for an aircraft propulsion engine where first and second hydraulic units are used to maintain a constant speed drive transmission.
  • US 4 960 085 discloses a pneumatic and electro-pneumatic pre-engage engine starter.
  • US 2008/0098732 discloses a hydraulic differential for an integrated drive generator.
  • the invention relates to a hydraulic log according to claim 1 and to a method of driving components within a turbomachine according to claim 10.
  • the disclosure relates to a hydraulic log, comprising: a valve that controls a flow of fluid within the hydraulic log to provide a rotational output from the hydraulic log that is different than a rotational input to the hydraulic log; and wherein the valve controls flow of fluid from a higher pressure area of the hydraulic log to a lower pressure area of the hydraulic log; a first plurality of pistons each having a stroke that is adjusted with a first wobbler plate to provide a rotational output from the hydraulic log that is different than a rotational input to the hydraulic log; a second plurality of pistons, wherein a stroke of the second plurality of pistons is configured to be adjusted with a second wobbler plate to provide a rotational output from the hydraulic log that is different than a rotational input to the hydraulic log; and a port plate which separates the hydraulic log into a first portion including the first wobbler plate and a second portion including the
  • An example method of driving components within a turbomachine includes: providing a first rotational input to a hydraulic log using a motor-generator when the motor-generator is in a motor mode of operation; and using a valve that controls flow within the hydraulic log to adjust the first rotational input to a second rotational input that drives a compressor rotor; wherein the hydraulic log comprises: a first wobbler plate to adjust a stroke of a first plurality of pistons; a second wobbler plate to adjust a stroke of a second plurality of pistons; and a port plate which separates the hydraulic log into a first portion including the first wobbler plate and a second portion including the second wobbler plate, the port plate having a first opening in a higher pressure area of the hydraulic log, and a second opening in a lower pressure area of the hydraulic log, the method further comprising: moving flow through the first opening from the first portion to the second portion; moving flow through the second opening from the second portion to the first portion; and controlling flow of fluid from the higher pressure area of
  • an example gas turbine engine 10 is used to propel an aircraft 12.
  • the gas turbine engine 10 is an example type of turbomachine.
  • the example gas turbine engine 10 includes (in serial flow communication) a fan section 14, a low pressure compressor 18, a high pressure compressor 22, a combustor 26, a high pressure turbine 30, and a low pressure turbine 34.
  • the gas turbine engine 10 is circumferentially disposed about an engine axis X.
  • air is pulled into the gas turbine engine 10 by the fan section 14. Some of the air moves through a flow path 36 to a core of the gas turbine engine 10.
  • the air moving through the flow path 36 is pressurized by the compressors 18 and 22, mixed with fuel, and burned within the combustor 26.
  • the turbines 30 and 34 extract energy from the hot combustion gases flowing from the combustor 26.
  • the high pressure turbine 30 utilizes the extracted energy from the hot combustion gases to power the high pressure compressor 22 through a high speed shaft 38
  • the low pressure turbine 34 utilizes the extracted energy from the hot combustion gases to power the low pressure compressor 18 and the fan section 14 through a low speed shaft 42.
  • the compressor sections 18 and 22 include a rotor assembly 40 having blades 44 connected to a shaft 48. Rotating the shaft 48 rotates the rotor blades. The rotor blades 44, when rotated, compress the air moving through the flow path 36.
  • the rotor assembly 40 rotates to compress air within the compressor sections 18 and 22 during start-up of the engine 10.
  • a motor-generator 54 continues to drive rotation of the rotor assembly 40 until the rotor assembly 40 reaches a speed capable of compressing enough air to sustain operation of the engine 10.
  • the turbines 30 and 34 are able to suitably drive the rotor assembly 40 without requiring the rotational input from the motor-generator 54 ( Figure 3 ).
  • the motor-generator 54 operates as a generator after the engine 10 has reached self-sustaining speed.
  • an arrangement 50 for driving the engine 10 of Figure 1 includes the motor-generator 54, a hydraulic log 58, and a gear differential 46.
  • the motor-generator 54 provides the rotational input to the hydraulic log 58 and differential 46 during start-up of the engine 10.
  • the engine 10 is configured to rotate the arrangement's input shaft 48, rather than the input shaft 48 rotating portions of the engine 10.
  • the hydraulic log 58 is configured to provide a rotational input to the differential 46.
  • the differential 46 then provides a rotational input to the motor-generator 54 so that the motor-generator 54 can operate as a generator and provide power in a known manner.
  • the aircraft 12 utilizes power from the motor-generator 54 to operate various devices on the aircraft 12.
  • a relatively consistent supply of power from the motor-generator 54 is required. Variations in the rotational speed of the input shaft 48 would vary the power output from the motor-generator 54 were it not for the hydraulic log 58.
  • the hydraulic log 58 in this example, accommodates the varying rotational speeds of the input shaft 48 and provides the motor-generator 54 with a relatively consistent rotational input such that the motor-generator 54 is able to provide a relatively consistent frequency source of power to the aircraft 12.
  • the hydraulic log 58 receives the rotational input from the motor-generator 54 during start-up of the engine 10. The hydraulic log 58 then provides a rotational output to the input shaft 48. The hydraulic log 58 adjusts the rotational input to a rotational output suitable for driving the engine 10. A person having skill in this art would understand a rotational output suitable for driving the input shaft 48 during start up of the engine 10.
  • the hydraulic log 58 accommodates variability in the rotational output provided by the motor-generator 54 during motor mode and the rotational input provided by the engine 10 during generator mode.
  • the motor-generator 54 in the example arrangement 50 includes a rotor 66 and stator 70 arranged about a motor centerline X 1 .
  • the motor-generator 54 rotates a gear 74 that is rotatably coupled to the differential 46.
  • the hydraulic log 58 includes a first plurality of pistons 82 and a second plurality of pistons 86.
  • a wobbler plate 90 controls the stroke length of the first plurality of pistons 82.
  • the wobbler plate 90 is adjusted relative to an axis X 2 of the hydraulic log 58 to change the stroke lengths of the plurality of pistons 82.
  • a wobbler plate 94 controls the stroke lengths of the second plurality of pistons 86.
  • the wobbler plate 94 is adjusted relative to the axis X 2 of the hydraulic log 58 to change the stroke lengths of the second plurality of pistons 86.
  • adjusting the strokes of the first plurality of pistons 82 and the second plurality of pistons 86 adjusts the rotation of a gear 78 relative to the rotation of the hydraulic log shaft 98.
  • the hydraulic log 58 is thus able to step up or step down rotation of gear 78 relative to the input shaft 48 speed by varying the positions of the wobbler plates 90 and 94.
  • the gear differential 46 sums the speed of gear 78 and the speed of the input shaft 48 and produces a resultant output speed on gear 80 to drive the motor-generator 54.
  • the relationship between the speed of gear 78, the speed of input shaft 48, and the speed of gear 80 is constant and is determined by the relative number of teeth on the gears within the differential 46. Proper control of gear 78 speed relative to the input shaft 48 speed produces a constant speed on gear 80 and on the motor-generator 54. Constant speed on the motor-generator 54 produces a constant frequency electric power output from the arrangement 50.
  • a controller 84 controls the positions of wobbler plates 90 and 94 via a control piston assembly 88 connected to each wobbler plate. For example, if the gear 74 is rotating too fast to supply constant frequency power from the motor-generator 54, the controller 84 initiates an adjustment to at least one of the wobbler plates 90 or 94 that causes gear 78 to slow its rotation. As can be appreciated, slowing the rotation of gear 78 slows rotation of gear 74 through the gear differential 46.
  • the wobbler plates 90 and 94 are connected to individual control piston assemblies 88 to enable movement over the range bounded by lines Y 1 and Y 3 .
  • the controller 84 varies the position of the wobbler plates 90 and 94 by varying the hydraulic pressure acting on the control pressure side of the piston 110.
  • the control piston assemblies 88 include biasing forces in the form of a spring 106 and hydraulic pressure against a piston 112.
  • the stator 70 of the motor-generator 54 is connected to an external electric power source.
  • the external power source causes the motor-generator 54 to act as an electric motor and accelerates the rotor 66.
  • the controller 84 initiates an adjustment to at least one of the wobbler plates 90 or 94 that allows the rotor 66 to accelerate while the input shaft 48 is stationary.
  • the hydraulic log 58 essentially free-wheels and provides minimal resistance to the motor-generator 54. This allows the rotor 66 to be accelerated with minimal drag torque and essentially declutches the rotor 66 from the input shaft 48 during initial acceleration.
  • a person having skill in this art would understand how this would allow significant size and weight savings for both the motor-generator 54 and the external electric power source.
  • controller 84 initiates adjustments to wobbler plate 90 to cause this half of the hydraulic log 58 to function as a hydraulic pump. Controller 84 controls wobbler plate 94 to cause this half of the hydraulic log 58 to function as a hydraulic motor in response to the working pressure generated by the plurality of pistons 82. Since the plurality of pistons 86 are stationary at the start of this sequence, working pressure rises as the plurality of pistons 82 pump oil against them.
  • the mechanical torque produced by the plurality of pistons 86 is transmitted via gear shaft 98 to the differential 46.
  • the gradual addition of torque to the differential 46 causes the input shaft 48 to accelerate and gear 78 to decelerate. Acceleration of input shaft 48 causes the gas turbine engine 10 to accelerate.
  • the hydraulic working pressure in hydraulic log 58 needs to be maintained to a level suitable for acceleration of the gas turbine engine 10.
  • the torque on the input shaft 48 peaks when the portion of the hydraulic log with wobbler plate 90 reaches maximum displacement, for example.
  • the remainder of the start cycle is then maintained at a constant power by limiting current to the motor-generator 54.
  • the controller 84 initiates adjustments to wobbler plate 90 which cause that half of the hydraulic log 58 to transition to a hydraulic motor. Simultaneously, the controller 84 initiates adjustments to wobbler plate 94 which cause that half of the hydraulic log 58 to transition to a hydraulic pump. Essentially, the two halves of the hydraulic log 58 switch roles as they transition from start mode to generate mode.
  • wobbler plate 90 is held in a position aligned with line Y 1 by the hydraulic bias pressure within control piston assembly 88.
  • controller 84 senses output frequency of the motor-generator 54 and varies the control pressure acting on the control piston assembly 88 to adjust the position of wobbler plate 94 as necessary to maintain a consistent speed of the motor-generator 54.
  • the controller 84 senses current to the motor-generator 54 to regulate movement of the wobbler plates 90 and 94 during the transition from start to generate mode. If the wobblers 90 and 94 are repositioned too fast, the motor-generator 54 current may undesirably climb. Further, if the wobbler plates 90 and 94 are repositioned too slow, the gas turbine engine 10 start could stall. A person skilled in this art could establish a proper relationship between the decay of current to the motor-generator 54 and the working pressure in the hydraulic log 58.
  • the position of the wobbler plate 90 when aligned with the line Y 2 corresponds to a motor-generator 54 acceleration mode of operation.
  • the position of the wobbler plate 90 when aligned with line Y 1 corresponds to a normal generator mode of operation.
  • the position of wobbler plate 90 when between line Y 2 and Y 3 corresponds to a start mode of operation during which the gas turbine engine 10 is being accelerated.
  • a port plate 92 separates the hydraulic log 58 into a first portion 114 (or half) that includes the wobbler plate 90 and a second portion 116 (or half) that includes the wobbler plate 94.
  • Openings 118 in the port plate 92 permit flow of hydraulic fluid between the first portion 114 and the second portion 116.
  • the openings 118 above the axis X 2 may communicate high pressure fluid from the first portion 114 to the second portion 116, and the openings 118 below the axis X 2 communicate low pressure fluid from the second portion 116 to the first portion 114.
  • the positioning of the wobbler plates 90 and 94 depends on whether the first portion 114 is operating as a pump or a motor, and whether the second portion 116 is operating as a pump or a motor depending on the direction of power flow and if the machine is in start or generate mode.
  • Adjusting the positions of the wobbler plates 90 and 94 adjusts the rotational speed of the motor-generator 54 relative to the input shaft 48.
  • both the valve 130, the wobbler plates 90 and 94, or both may be used to adjust the speed of the motor-generator 54 relative to the input shaft 48, rather than exclusively the wobbler plates 90 and 94.
  • a controller 84a controls a valve 130 to adjust the speed of the motor-generator 54 relative to the input shaft 48.
  • a hydraulic log 58a generally includes a higher (working) pressure area 120 and a lower pressure area 122. These portions alternate being above or below the axis X 2 depending on whether the first portion 114 is operating as a pump or a motor, and whether the second portion 118 is operating as a pump or a motor, and if operating in start or generate mode.
  • the valve 130 selectively permits fluid to move from the higher pressure area 120 of the hydraulic log 58 to the lower pressure area 122. In so doing, the valve 130 regulates the working pressure and adjusts the relative differences in the rotational speed between the input shaft 48 and the motor generator 54 without requiring adjustments to either of the wobbler plates 90 or 94.
  • the working pressure in the hydraulics of the hydraulic log 58a during start-up is a function of the torque being generated, the set displacement of the 'motoring' side (amount of stroke on variable unit during start), and the difference in actual rotational speeds of the hydraulic units from the speeds commanded by the stroke.
  • valve 130 of the arrangement 58a may be used instead of, or in addition to, the control piston assembly 88.
  • the portion of the hydraulic log 58 functioning as a pump has a rate of change in displacement that is set by the rate which would set a constant working pressure during start-up.
  • the hydraulic unit driving the engine 10 speeds up causing working pressure within the hydraulic log 58 to decrease.
  • the stroke of pistons in this portion of the hydraulic log 58 automatically advances in response to reduced bias pressure, which causes an increase in speed, torque, and working pressure until reaching a set bias level.
  • This set bias level sets the maximum working pressure to safe limits, but also limited the amount of torque produced at certain speeds because the stroke (displacement) was limited to provide the safe working pressure limits.
  • the torque generated would change as the displacements (stroke) of the hydraulic units changed, even though working pressure remained nearly constant.
  • the bias pressure on the back side of the control piston 88 may be replaced with the valve 130.
  • This characteristic allows the displacement (stroke) to be set to a maximum and held there during the start-up, and allow the valve 130 to regulate the working pressure.
  • the valve 130 includes a biasing member 132.
  • the biasing member 132 is configured to bias the valve 130 toward a restrictive flow position 138.
  • the pressure in the working pressure area 120 of the hydraulic log 58 increases to a certain level, the pressure overcomes the biasing force exerted by the biasing member 132 and causes the valve 130 to move to a less restrictive flow position 142.
  • the less restrictive flow position 142 permits more hydraulic fluid to move from the higher pressure area 120 of the hydraulic log 58 to the low pressure area 122 than when the valve 130 is in the more restrictive flow position 138.
  • hydraulic fluid continues to move from the working pressure area 120 to the lower pressure area 122 until the pressure in the working pressure area 120 drops to a point below the biasing force of the biasing member 132.
  • valve 130 When the valve 130 is in the more restrictive position 138, hydraulic fluid still may move through the openings 118. Using the valve 130 in conjunction with the hydraulic log 58 effectively increases the area permitting flow between the various areas of the hydraulic log 58. As appreciated, pressure differentials between working pressure area 120 and the low pressure area 122 provide the relative adjustments in rotational speed and torque.
  • wobbler plates 94 and 90 dictates the portion of the hydraulic log 58 that is the working pressure area 120 or the low pressure area 122.
  • the wobbler plates 90 and 94 are alternated between a fully opened and a fully closed position depending on whether the motor generator 54 is driving the input shaft 48, or whether the input shaft 48 is driving the motor generator 54. The finer adjustments in the relative speeds and regulating working pressure are then accomplished utilizing the valve 130.
  • the valve 130a is a solenoid valve that is operatively linked to the controller 84a.
  • the controller 84a adjusts the positioning of the solenoid valve to permit a desired amount of flow through the valve 130, thus actively controlling the working pressure and speed.
  • Additional features of the disclosed examples include using a motor-generator to start an engine and to provide electric power to the engine during different modes of operation. Another feature includes a lower weight and lower cost design when compared to other motor-generator options.
  • SDG starter-drive generator

Claims (12)

  1. Unité hydraulique, comprenant :
    une soupape (130) qui régule un écoulement de fluide au sein de l'unité hydraulique (58) pour fournir une sortie de rotation depuis l'unité hydraulique qui est différente d'une entrée de rotation dans l'unité hydraulique, dans laquelle la soupape (130) régule un écoulement de fluide depuis une zone de pression plus élevée (120) de l'unité hydraulique (58) jusqu'à une zone de pression plus faible (122) de l'unité hydraulique (58) ; et
    une première pluralité de pistons (82, 86) ayant chacun une course qui est ajustée avec une première plaque à bascule (90, 94) pour fournir une sortie de rotation depuis l'unité hydraulique qui est différente d'une entrée de rotation dans l'unité hydraulique ;
    une seconde pluralité de pistons (82, 86) dans laquelle une course de la seconde pluralité de pistons est configurée pour être ajustée avec une seconde plaque à bascule (90, 94) pour fournir une sortie de rotation depuis l'unité hydraulique qui est différente d'une entrée de rotation dans l'unité hydraulique ; et
    une plaque à orifices (92) qui sépare l'unité hydraulique en une première portion (114) comportant la première plaque à bascule et une seconde portion (116) comportant la seconde plaque à bascule, la plaque à orifices ayant une première ouverture (118) pour permettre un écoulement de la première portion à la seconde portion et une seconde ouverture (118) pour permettre un écoulement de la seconde portion à la première portion ;
    et dans laquelle la première ouverture se trouve dans la zone de pression plus élevée (120) de l'unité hydraulique et la seconde ouverture se trouve dans la zone de pression plus faible (122) de l'unité hydraulique.
  2. Unité hydraulique selon la revendication 1, dans laquelle la soupape (130) comprend un organe de sollicitation (132).
  3. Unité hydraulique selon la revendication 1, dans laquelle la soupape (130) comprend un solénoïde.
  4. Unité hydraulique selon une quelconque revendication précédente, dans laquelle la soupape (130) est ajustée par un dispositif de régulation (84) pour réguler de façon sélective un écoulement de fluide au sein de l'unité hydraulique (54).
  5. Unité hydraulique selon une quelconque revendication précédente, dans laquelle l'unité hydraulique (58) accouple en rotation un rotor de turbomachine (40) et un moteur-générateur (54).
  6. Unité hydraulique selon une quelconque revendication précédente, dans laquelle l'unité hydraulique (58) est accouplée en rotation à un moteur-générateur (54) qui a un mode de fonctionnement moteur et un mode de fonctionnement générateur, dans laquelle le moteur-générateur est configuré pour entraîner l'arbre d'entrée (48) à travers l'ensemble unité hydraulique lorsque le moteur-générateur est dans le mode de fonctionnement moteur, et l'arbre d'entrée est configuré pour entraîner le moteur-générateur à travers l'unité hydraulique lorsque le moteur-générateur est dans le mode de fonctionnement générateur.
  7. Unité hydraulique selon la revendication 6, dans laquelle la soupape (130) est configurée pour ajuster l'entrée de rotation provenant du moteur-générateur (54) pour entraîner l'arbre d'entrée (48) lorsque le moteur-générateur est dans le mode de fonctionnement moteur ; et/ou
    dans laquelle la soupape (130) est configurée pour ajuster l'entrée de rotation provenant de l'arbre d'entrée (48) pour fournir une sortie de rotation qui entraîne le moteur-générateur (54) lorsque le moteur-générateur est dans le mode de fonctionnement générateur.
  8. Ensemble moteur à turbine à gaz, comprenant :
    un moteur-générateur (54) ;
    un rotor de compresseur (40) ; et
    l'unité hydraulique (58) de l'une quelconque des revendications 1 à 4 qui reçoit une entrée de rotation depuis l'un du moteur-générateur ou du rotor de compresseur, et fournit une sortie de rotation à l'autre du moteur-générateur ou du rotor de compresseur ;
    dans lequel la soupape ajuste un écoulement entre des zones de l'unité hydraulique pour ajuster sélectivement la vitesse de la sortie de rotation par rapport à la vitesse d'entrée de rotation.
  9. Ensemble moteur à turbine à gaz selon la revendication 8, dans lequel la soupape (130) ajuste sélectivement la vitesse de la sortie de rotation par rapport à l'entrée de rotation indépendamment des première et seconde pluralités de pistons (82, 86).
  10. Procédé d'entraînement de composants au sein d'une turbomachine, comprenant :
    la fourniture d'une première entrée de rotation à une unité hydraulique (58) à l'aide d'un moteur-générateur (54) lorsque le moteur-générateur est dans un mode de fonctionnement moteur ; et
    l'utilisation d'une soupape (130) qui régule un écoulement au sein d'une unité hydraulique pour ajuster la première entrée de rotation à une deuxième entrée de rotation qui entraîne un rotor de compresseur (40) ;
    dans lequel l'unité hydraulique (58) comprend :
    une première plaque à bascule (90, 94) pour ajuster une course d'une première pluralité de pistons (82, 86) ;
    une seconde plaque à bascule (90, 94) pour ajuster une course d'une seconde pluralité de pistons (82, 86) ; et
    une plaque à orifices (92) qui sépare l'unité hydraulique en une première portion (114) comportant la première plaque à bascule et une seconde portion (116) comportant la seconde plaque à bascule, la plaque à orifices ayant une première ouverture (118) dans une zone de pression plus élevée (120) de l'unité hydraulique, et une seconde ouverture (118) dans une zone de pression plus faible (122) de l'unité hydraulique,
    le procédé comprenant en outre :
    le déplacement d'un écoulement à travers la première ouverture de la première portion à la seconde portion ;
    le déplacement d'un écoulement à travers la seconde ouverture de la seconde portion à la première portion ; et
    la régulation d'un écoulement de fluide de la zone de pression plus élevée (120) de l'unité hydraulique (58) à la zone de pression plus faible (122) de l'unité hydraulique (58) à l'aide de la soupape.
  11. Procédé selon la revendication 10, comportant en outre,
    la fourniture d'une troisième entrée de rotation dans l'unité hydraulique (58) à l'aide du rotor de compresseur (40) lorsque le moteur-générateur (54) est dans un mode de fonctionnement générateur ; et
    l'utilisation de la soupape (130) qui régule un écoulement au sein de l'unité hydraulique pour ajuster la troisième entrée de rotation et pour fournir une quatrième entrée de rotation qui entraîne le moteur-générateur ;
    dans lequel l'unité hydraulique comprend plus d'une plaque à bascule (90, 94).
  12. Procédé selon la revendication 10 ou 11, dans lequel l'utilisation de la soupape (130) comprend en outre la sollicitation de la soupape en éloignement d'une position d'autorisation d'écoulement vers une position de limitation d'écoulement via un organe de sollicitation (132).
EP13157705.8A 2012-03-05 2013-03-04 Dispositif d'entraînement d'une turbomachine Active EP2636872B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US13/411,920 US9394831B2 (en) 2010-03-17 2012-03-05 Turbomachine drive arrangement

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EP2636872A2 EP2636872A2 (fr) 2013-09-11
EP2636872A3 EP2636872A3 (fr) 2017-12-20
EP2636872B1 true EP2636872B1 (fr) 2019-05-01

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EP13157705.8A Active EP2636872B1 (fr) 2012-03-05 2013-03-04 Dispositif d'entraînement d'une turbomachine

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US10763722B2 (en) * 2018-01-11 2020-09-01 Hamilton Sundstrand Corporation Terminal block for use in integrated drive generator
US11002258B2 (en) 2018-01-18 2021-05-11 Hamilton Sundstrand Corporation Port plate for integrated drive generator

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US4315442A (en) * 1980-02-15 1982-02-16 Sundstrand Corporation Aircraft generator starter-drive
US4960085A (en) * 1988-08-31 1990-10-02 Tech Development Inc. Pneumatic and electro-pneumatic starters
US4922119A (en) * 1988-11-29 1990-05-01 Sundstrand Corporation Integrated starting system
US7472547B2 (en) * 2006-10-26 2009-01-06 Hamilton Sundstrand Corporation Hydraulic differential for integrated drive generator
US20110225978A1 (en) * 2010-03-17 2011-09-22 Behling David S Turbomachine drive arrangement

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EP2636872A2 (fr) 2013-09-11

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